US3890019A - Magnetic bearings - Google Patents

Magnetic bearings Download PDF

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US3890019A
US3890019A US342892A US34289273A US3890019A US 3890019 A US3890019 A US 3890019A US 342892 A US342892 A US 342892A US 34289273 A US34289273 A US 34289273A US 3890019 A US3890019 A US 3890019A
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Prior art keywords
bearing
bearing according
magnetic
flux path
ferromagnetic
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US342892A
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Karl Boden
Dietrich Scheffer
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Padana AG
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Padana AG
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C32/00—Bearings not otherwise provided for
    • F16C32/04—Bearings not otherwise provided for using magnetic or electric supporting means
    • F16C32/0406—Magnetic bearings
    • F16C32/044—Active magnetic bearings
    • F16C32/0459—Details of the magnetic circuit
    • F16C32/0461—Details of the magnetic circuit of stationary parts of the magnetic circuit
    • F16C32/0465—Details of the magnetic circuit of stationary parts of the magnetic circuit with permanent magnets provided in the magnetic circuit of the electromagnets
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C32/00—Bearings not otherwise provided for
    • F16C32/04—Bearings not otherwise provided for using magnetic or electric supporting means
    • F16C32/0406—Magnetic bearings
    • F16C32/044—Active magnetic bearings
    • F16C32/0474—Active magnetic bearings for rotary movement
    • F16C32/0476—Active magnetic bearings for rotary movement with active support of one degree of freedom, e.g. axial magnetic bearings

Definitions

  • a magnetic bearing is provided with two, at least partly separated, flux paths; one for the magnetic field of a permanent magnet and the other for the magnetic field of an electrical winding.
  • the electromagnetic flux path includes a ferromagnetic part having a high permeability so that the electromagnetic field can be varied with the use of a relatively low input energy to the electrical winding.
  • the two fields are superimposed upon one another in two air gaps between the bearing
  • the invention is applicable to linear bearings, axial bearings and radial rotary bearings.
  • the invention relates to a magnetic bearing for supporting a body by applying a controllable magnetic field to the body.
  • the magnetic reluctance of the flux path of the electrically produced magnetic field is extremely high because the flux paths for the permanent magnetic and the electromagnetic fields are the same.
  • the electromagnetic field is conducted, with the exception of the body to be journalled, exclusively through media having high reluctance because permanent magnetic material in the stable range of its magnetizing characteristic has a low permeability (plof the order of unity).
  • a very high electromagnetic coupling Ampere-turns
  • Increasing the amplitude of the electromagnetic regulating fields can also lead to demagnetization of the permanent magnets.
  • a magnetic bearing for a body at least a portion of which is ferromagnetic comprises at least one permanent magnet for producing a magnetic field along a first flux path and an electromagnet winding for producing a magnetic field along a second flux path, whereby a controllable magnetic field is applied to said ferromagnetic body or portion thereof, the ferromagnetic part of the bearing through which the electromagnetic flux path passes offering a high permeability to the magnetic filed produced by said electromagnet winding.
  • the permanent magnetic and the electromagnetic flux paths are at least partly separated and can be arranged partly parallel to one another in the same or opposing directions.
  • the ferromagnetic material in the electromagnetic flux path has high permeability which is necessary for a low reluctance thus leading to a saving on regulating energy.
  • the permanent magnetic premagnetization exerts very high attractive forces on the body in relation to the electrical energy.
  • the regulating field is preferably superimposed on the premagnetization in the air gap. The effect is thus utilized that the attractive force varies as the square of the magnetic induction B. From theoretical considerations, ignoring fringe effects, the force raising effect of the premagnetization can be appreciated from the following examples. It is first assumed that a permanent magnetic field with an induction having the arbitrary value prevails in the air gap.
  • a regulating field of i2 had been used without premagnetization a force of the value of 4 would have been obtained.
  • the premagnetization does not require the continuous consumption of energy, so that for a given use of electrical energy greater magnetic field energizes and attractive forces can be achieved.
  • the first and second flux paths both extend through the gap or gaps between the body and the bearing where they are substantially parallel to one another and commonly situated.
  • the permanent magnetic flux path is completed through two ferromagnetic parts which are thereby at least partly magnetized into their region of magnetic saturation, which ferromagnetic parts lie at the same time in the electromagnetic flux path, the field of the electromagnetic winding being in the same direction as that of the permanent magnet or magnets in one ferromagnetic part but in the opposite direction to that of the permanent magnet or magnets in the other ferromagnetic part.
  • the permanent magnetic flux path contains at least two permanent magnets arranged side-byside with unlike poles next to one another and two ferromagnetic parts overlying the pole faces.
  • the magnetic field produced in the two ferromagnetic parts by the oppositely directed side-by-side magnets saturates these parts.
  • the electro-magnetic field is added to the permanent magnetic field in one of the two parts and subtracted in the other part.
  • the magnetic conductivity is very low (the reluctance is very high) whilst the opposite is the case for the other part.
  • the latter remains in the range of ferromagnetism.
  • Corresponding changes take place in the magnetic field produced by the electrical current in the Winding so that correspondingly lower or higher field strengths prevail in the adjacent air gaps.
  • FIG. 1 is a schematic longitudinal sectional view of a contactless magnetic bearing system for a rotating body
  • FIG. 2 is a schematic axial section of the magnetic axial bearing according to one embodiment of the invention.
  • FIG. 3 is a schematic longitudinal section of another embodiment of magnetic axial bearing
  • FIG. 4 is a schematic perspective sectional view of a linear bearing in accordance with the invention.
  • FIG. 5 is a perspective sectional view of another embodiment of linear bearing
  • FIG. 6 is a schematic detail section for explaining the mode of operation of other magnetic bearings of the invention.
  • FIGS. 7 and 8 are schematic perspective sectional views of two further embodiments of linear bearings
  • FIG. 9 is a detail cross-section on the line IXIX of FIG. 8;
  • FIG. 10 is a schematic perspective sectional view of a linear bearing which permits stabilisation in the presence of a rotary degree of freedom
  • FIG. 11 is a perspective sectional detail of another embodiment of axial hearing. I
  • FIG. 12 is a longitudinal section of a further embodiment of axial bearing.
  • FIG. 13 is a detail sectional view of yet bodiment of the invention.
  • FIG. 1 a body 13 in the form ofa rotor journalled abouta vertical rotary axis 14. It is journalled without contact by means of a magnetic bearing system which comprises two radial bearings 15 suranother emrounding the upper and lower parts of the rotor 13 and an axial stabilising magnet 16.
  • a magnetic bearing system which comprises two radial bearings 15 suranother emrounding the upper and lower parts of the rotor 13 and an axial stabilising magnet 16.
  • the axial stabilising magnet comprises an annular permanent magnet which, in cooperation with an edge 17 of the ferromagnetic rotor brings about an axially stable, but radially unstable, support for the rotor.
  • the electromagnetic means are provided with output signals from a controller 18 which generates these output signals in dependence upon sensor signals which are in turn produced by sensors 19 in response to changes in the spacing of these sensors from the rotor.
  • the controller 18 is a dc controller and comprises an amplifier and a phase displacer whose output signals are advanced in phase with respect to time by a certain amount with respect to the sensor signals, which amount normally lies between zero and a quarter of the oscillation period of the sensor signals.
  • the radial bearing 15 and the axial stabilising magnet 16 are generally secured to, or part of, a stator 20 or other fixed part illustrated as a housing.
  • the upper end 24 of the rotor 13 is provided with an annular groove 21 into which a bearing element 22 extends.
  • This bearing element 22 in the present case is constructed as an axial bearing element and can have, for example, the individual features shown in FIG. 12,
  • Thebearingelement 22 produces formed between the edge 17 and the bearing element 22, and betweenthe upper surface 23 of the groove 21 and the bearing element 22, and serves to hold the rotor with exact precision in axial position.
  • the rotor 13 is to be held in an axially'stable position by the axial stabilising magnet 16 so that with the present bearing system with a vertical rotary axis the weight forces are opposed by corresponding counter-forces.
  • the axial damping energy due to eddy currents and hysteresis losses which occur in most cases when the axial position is not so exactly maintained, doesnot produce any substantially varying forces in this direction.
  • the axial bearing element 22 is thus provided in order to obtain exact axial position of the rotor.
  • this bearing applies a regulated magnetic field.
  • an active regulated magnetic field will be provided, that is, a magnetic field regulated automatically according to position.
  • the bearing element 22 it is also possible for the bearing element 22 to be readily after-adjustable by means of a few additional measures in that, for example, an afterregulation of the axial bearing can be obtained by hand.
  • a controller 27 is connected to the bearing element 22 and essentially corresponds to the already described controllers 18.
  • the controller 27 is supplied with sensor signals from a sensor 28 which has a contactless proximity detector disposed on the stator 20.
  • the sensor 28 converts displacement of the rotor from its desired axial position into sensor signals. It can, for example, be an inductive, capacitive or photoelectric sensor. The use of galvanomagnetic constructional elements is also possible.
  • the controller 27 is a dc. controller and contains an amplifier and a phase displacer.
  • the sensor signals are converted in the controller 27 into output signals which are advanced in phase relative to the sensor signals by an amount between zero and a quarter of the oscillation period of the sensor signals.
  • the output signals are do. signals, that is, the fluctuations in current or voltage amplitude are simply causedby displacements or oscillations of the rotor. No carrier frequency is used.
  • This kind of regulation which is also used by the radial bearings 15, has a great advantage that the losses due to the magnetic flux reversals in the rotor are reduced. It is thus possible for the rotor to be made out of any desired ferromagnetic material, for example, ordinary steel. The use of rotor laminations or other measures for minimising losses due to magnetic field reversal is generally not necessary.
  • the application of the output signals by the controller 27 to the bearing elements produces magnetic fields operating on the rotor, and thus applies forces to the rotor.
  • These forces can be divided into two components, namely a compensating force component which 1 is in phase with the sensor signals and serves for returncollar 29 whose upper and lower surfaces 30 and 31 limit upper and lower air gaps 25 and 26 respectively.
  • the fixed surfaces of the air gaps are formed on an annular non-rotating ferromagnetic part 32 formed of a material with high permeability (p 1000).
  • the material may, for example, be iron or steel of suitable quality, highly permeable compressed material or, in special cases, individual sheets (dynamo sheet) electrically insulated from one another.
  • the important thing in each case is for the part 32 to have good magnetic conductivity. Within such considerations, the choise of material will depend upon the use of the apparatus which is fitted with the bearing system.
  • the part 32 is substantially annular with a U-shaped cross-section providing an internal groove.
  • the part 32 is formed of a core 33 in the form of an external ring, and shanks adjoining this ring and forming poles 34 and 35. These poles at the same time provide the fixed surfaces defining the air gaps 25 and 26.
  • the part 32 is secured to the stator 20 (only a detail of which is illustrated).
  • the radial bearings for the rotor 13 can be as illustrated in FIG. 1.
  • An electrical winding 36 is provided on the core 33 and in the illustrated embodiment is provided internally and externally of the core 33 so as to completely embrace the part 32. It will be appreciated that the winding 36 may take various forms in that it may, for example, be provided only internally or only externally of the core 33, or may be provided in the form of individual coils. Whatever form of winding is used, however, it must produce in the core 33 a variable magnetic field whose lines of force pass from one pole to the other. The path of these lines of force is hereinafter referred to as the electromagnetic flux path 37 and is shown in the drawings by dash-dot lines. Arrows indicate the direction of the lines of force.
  • the winding 36 is connected to the controller 27 by means not shown.
  • the associated sensor 28 is not shown in FIG. 2. It can cooperate with any desired part of the rotor in order to determine its axial position.
  • the electromagnetic flux path 37 passes through the core 33 and is completed through the poles 34, 35, the air gaps 25, 26 and the ferromagnetic collar 29.
  • Permanent magnets 38, 39 are arranged in the axial direction outside the poles 34, 35. They comprise annular magnets of ferrite compressed material and are axially polarised. Each produces a respective magnetic field along a respective magnetic flux path 40, 41 whose approximate line and direction are likewise indicated by dash-dot lines and by arrows.
  • the flux paths 37, 40, 41 are closed flux paths and in the illustrated embodiment are somewhat toroidal in shape.
  • the permanent magnets 38, 39 are so arranged that like magnet poles face the poles 34, in the illustrated embodiment the North magnetic poles.
  • the permanent magnetic field is such that the premagnetisation field symbolised by the magnetic flux path is strengthened in the upper air gap 25 when electrical current is applied to the winding 36 of the electromagnetic flux path 37 in the direction or orientation indicated in FIG. 2.
  • the electromagnetic flux path 37 is superimposed upon the permanent magnetic flux path 41 so that an increased attractive force in the air gap 25, and a decreased attractive force in the air gap 26, are exerted upon the rotor so that the rotor is drawn upwards.
  • the bearing 22 need only be provided with a relatively small quantity of energy for control or regulating purposes. For one reason it is not necessary that the winding 36 be supplied with a constant bias current whose amplitude is regulated, rather an energy saving regulation by current reversal is not only possible, but advantageous. Nevertheless, regulation by means of a bias current is possible whereby it is possible to adjust the load carrying capacity of the bearing.
  • the electromagnetic flux path 37 has a minimum magnetic reluctance in that it is composed almost entirely of the high permeability part 32 and the likewise ferromagnetic rotor part 29 also of high permeability. The magnetic flux easily bridges the air gaps 25, 26 which in the drawing have been grossly exaggerated.
  • the permanent magnetic flux path 40 is substantially completely separated from the magnetic flux path 37. Both flux paths can simply run parallel to one another in the air gaps 25, 26 so that mutual strengthening or weakening is possible.
  • the lower permeability of the material of the permanent magnets 38, 39 does not have any disadvantageous influence upon the electromagnetic flux path 37. There is also no tendency for the permanent magnets 38, 39 to be demagnetised by greatly and strongly alternating magnetic fields in the flux path 37.
  • the bearing 22 illustrated in FIG. 3 is in basic construction and operation similar to that of FIG. 2 and does not, therefore, require further detailed description. Parts of the embodiment of FIG. 3 like those of FIG. 2 are indicated by like references.
  • the rotor 13 is provided with a collar 29 which in this embodiment is inwardly directed.
  • the part 32 has the shape of a spool, that is, it is annular with a U-shaped cross-section to define an external groove 42.
  • the winding 36 is wound about the core of the spool.
  • the bearing 22 is fixed from above and the collar 29 on the rotor extends into the groove 42.
  • FIG. 4 of the drawings illustrates the same principle in connection with a linear bearing.
  • the part 32 in this case has the form of an elongated rail of U-shaped cross-section.
  • the core 33 forming the base of the U- shaped cross-section carries the current conducting winding 36.
  • the permanent magnets 38, 39 are likewise elongated and are in the form of strips.
  • the rotor 13 in this embodiment also has the shape of a strip or rail and extends into the U-shaped cross-section part 32
  • the whole bearing system has a certain length depending upon the relationships.
  • the winding 36 can i have an elongated oval shape.
  • the bearing illustrated in FIG. 4 makes possible stabilisation in a horizontal degree of freedom as indicated in the drawing in both orientations to the left and right.
  • sensors have to be arranged in this direction between fixed and movable parts. If the body 13 is so long that it can extend between at least two separate bearings of the kind shown in FIG. 4, then by varying regulation of these two bearings 22 stabilisation in a rotary degree of freedom about an axis which is vertical in FIG. 4 is possible.
  • the bearing 22 could be. the movable part whilst the body 13 is fixed.
  • FIG. shows a doubled-up form of the embodiment of FIG. 4 in that the part 32 is not U-shaped in section, but H-shaped.
  • the core 33 is thereby formed bythe web whilst the poles 34, 34 and 35, 35 are formed by the flanges.
  • the permanent magnets 38, 39 are each in the form of a broad plate disposed on the whole of the outside of the respective flange. Nevertheless, they could be formed as separate strips each covering a respective pole.
  • a respective body portion l3, I3 is arranged in the groove between the poles 34, 35 or 34, 35' and such portions may be joined together to form a C-shaped rail 43.
  • FIGS. 6 to 12 are constructed in accordance with similar principles with at least two magnetic flux paths separate from one another.
  • FIG. 6 illustrates the mode of operation of the embodiments of FIGS. 7 to 12.
  • the bearing 52 comprises permanent magnets 68, 69 of which two are shown in FIG. 6. They are arranged side-by-side with their pole faces 44 lying in common planes, but with unlike poles adjacent one another.
  • the magnetic axes of the permanent magnets 68, 69 are, therefore, parallel to one another, but in opposite directions.
  • the pole faces 44 of the permanent magnets 68, 69 are covered by ferromagnetic parts 62, 63 of one of the materials mentioned previously in connection with the part 32.
  • These parts 62, 63 are shown as being constructed of conductive sheet of relatively small crosssection so that the magnetic field in the permanent magnetic flux path 70, which is completed through the permanent magnet 68, the part 62, the permanent magnet 69 and the part 63, magnetises the parts 62, 63 substantially into their region of magnetic saturation. This saturation is at its maximum at the point adjacent the two surfaces 45 by which the magnets 68 and 69 lie against one another.
  • the magnetic flux should be sufficiently strong for the parts 62, 63 to be magnetised beyond saturation by an electromagnetic field superimposed upon the'permanentmagnetic fieldin the parts 62, 63.
  • a winding 66 can be arranged in various ways. The important thing is for the winding 66 to be able to readily produce an electromagnetic field in the unit 1 comprising the permanent magnets and ferromagnetic parts with the electromagnetic field parallel to the permanent magnetic field.
  • the electromagnetic flux paths 57 and 67 are indicated in FIG. 6. It is to be noted that in the embodiment as illustrated in FIG.
  • the lines of force in the flux paths 57 and 70 are parallel to one another, but in opposing directions in the part 62 whilst the lines of force in the corresponding flux paths 67 and 70 are likewise parallel to one another, but in the same direction in the part 63.
  • the part 62 is brought into a magnetic state in a region below magnetic saturation whereas the magnetic field strength in the part 63 is raised above the saturation field strength producedby the permanentmagnetic magnetisation..
  • the magnetic conductivity of this part .63 is, therefore,
  • the magnetic flux produced in the conductive plate 63 by the winding 66 is, therefore, very low, and that produced by the winding in the conductive plate v63 is very high, that is, in the re-' gion of that of ferromagnetic material with a permeability of a approximately equal to one thousand. Due to the relatively small magnetic reluctance of the conductive plate 62, the field strength in this plate due to the electromagnetic excitation by the winding 66is very high, and correspondingly the magnetic field strength in the adjoining air gap 25 is also high. The electromagnetic flux path 57 is completed through the body 13. The attractive force in the region of the air gap 25 is, therefore, substantially higher than that in the air gap 26. By reversing the flow of current through the winding 66 the opposite effect can be achieved.
  • the force raising and energy saving effects due to the premagnetisation can also be used.
  • the premagnetisation permanent magnetic field is extended into the air gapsso that the electromagnetic flux path can be superimposed upon the permanent magnetic flux path in these air gaps as described previously.
  • the fields can be strengthened or weakened in opposition to one another in the desired manner.
  • the premagnetisation through the separate permanent magnetic flux path 70 also has two functions. Firstly, it serves to magnetise the conductive plates 62, 63 into their region of saturation which is necessary for the operation of this embodiment. Secondly, it serves to create a permanent premagnetisation in the air gap which leads to the previously mentioned saving in control energy.
  • the bearing 52 shown in FIG. 7 of the drawings serves as a linear bearing.
  • the surfaces 46 by which the permanent magnets 68, 69 abut one another are substantially parallel to the direction of movement 45.
  • the ferromagnetic parts 62, 63 cover the laterally arranged pole faces of the permanent magnets and are provided with the winding 66 exteriorly. In this case the winding 66 limits the possible unbroken length of the bearing 52. It should be noted that in this case no variation or hardly any alternation of the magnetic fields takes place in the direction of movement 45.
  • the field is substantially homogeneous so that the hysteresis and eddy current losses in the body 13 are very low.
  • FIGS. 8 and 9 can be very simply constructed. It can be seen that permanent magnets 68 and 69 are arranged side-by-side one after the other in the direction of movement 45, the direction of magnetisation being horizontal, but adjacent magnets being polarised in opposite directions.
  • the bearing 52 can comprise numerous magnets 68, 69 arranged one after the other.
  • Two strip-like ferromagnetic parts 62, 63 cover the pole faces 44 of the magnets. Contrary to the winding arrangement of FIG. 7, the winding 66 of FIGS.
  • winding 8 and 9 is annular and is disposed about the parts 62 and 63 and the permanent magnets 68 and 69 sandwiched therebetween, so that the winding is, in effect, in the form of a long spiral whose axis extends in the direction of movement 45.
  • the winding 66 is separated or connected in sections 47, 48 as can be seen in FIG. 9.
  • Adjoining sections 47, 48 are wound in opposite directions.
  • Each winding section 47, 48 is symmetrically arranged about the plane in which the abutting surfaces 46 of adjoining magnets 68, 69 abut one another transversely to the direction of movement 45.
  • the lines of force in the body 13 are substantially perpendicular to its direction of movement 45, in that they, for example, enter the body near the top thereof and again enter the bearing element 52 adjacent the ends of the shanks of the body 13, in the embodiment of FIGS. 8 and 9 the lines of force enter and leave the body at points longitudinally spaced in the direction of movement 45.
  • the magnetic field is alternated at each coil section 47, 48, so that when movement takes place losses due to magnetic reversal occur in the body 13.
  • the embodiment of FIGS. 8 and 9, therefore, is only to be preferred if such losses become unimportant, for example, when the movements are slow or the magnetic forces are small.
  • FIG. 10 illustrates an embodiment which differs from that of FIGS. 8 and 9 simply in that the longitudinal groove formed in the rail-like body 13 is deeper, so as to receive two substantially identical bearings 52.
  • two bearings 52 with separate controllers and sensors, to controllably support the body in a horizontal translatory degree of freedom and in a rotary degree of freedom about an axis in the direction of movement 45.
  • FIGS. 7 to 10 are linear bearings operating upon the principles described with reference to FIG. 6.
  • FIGS. 11 and 12 illustrate axial bearings for a rotatable body.
  • the embodiment of FIG. 11 employs permanent magnets 68, 69 arranged one after the other similarly to the embodiment of FIGS. 8 and 9, but in a circle rather than in a straight line.
  • the axial bearing of FIG. 11 is generally only to be preferred for slow rotary movements.
  • the bearing shown in FIG. 12 is constructed similarly to that of FIG. 7.
  • Thepermanent magnets comprise two concentric rings arranged one within the other, but polarised in opposite axial directions.
  • the ferromagnetic parts 62, 63 this time in the form of hollow discs, lie against the end faces of the permanent magnets 68, 69.
  • the disc-like parts 62, 63 have a shallow U-shaped cross-section to form channels 49 in which the annular or spiral winding 66 lies.
  • the shape of the parts 62, 63 illustrated in FIG. 12 makes possible smaller air gaps and the shanks of the shallow U-shaped cross-section effectively operate as pole shoes.
  • the strong premagnetisation field of the permanent magnets is completely rotary symmetrical so that no losses due to magnetic reversal take place.
  • the construction of the rotors shown in FIGS. 11 and 12 is substantially as described above with reference to FIG. 1.
  • a bearing for magnetic bearing systems which is of simple construction and possesses relatively uncomplicated electrical parts.
  • the bearing possesses good reliability and operating safety.
  • the bearing is especially suitable as an axial bearing wherein it is advantageous that the axial forces can be applied in both axial directions at a single point in the rotor.
  • the control in both directions is possible by means ofjust one bearing with one winding.
  • very homogeneous magnetic fields can be produced without taking any special steps in connection with the rotor, and in particular with the material of the rotor.
  • no close limitations are placed upon the shape of the rotor.
  • the rotor can be constructed free of permanent magnets which not only would add additional weight, but would also reduce the rotary speed limit of the rotor.
  • damping and spring or suspension stiffness can be varied over wide limits. Electrical axial adjustment as accurate as mechanical adjustment is obtainable.
  • the ratio of useful inductivity to stray inductivity is very high, which is of specially great advantage for linear bearings in comparison with previously known linear bearings. Whilst the invention has been described in relation to bearing systems providing completely contact-free support of moving bodies, the bearing of the present invention can also be used in bearing systems which are not completely free of mechanical contact.
  • FIG. 13 of the drawings illustrates an embodiment of the invention which comprises a radial bearing which is magnetically actively controllable.
  • the axial length of the core 100 is larger than its radial thickness.
  • the coiled or toroidal winding may, for example, comprise four parts, each occupying a quarter of the circumference of the core 105.
  • the coils into which the winding is thus separated or divided are connected to a corresponding controller.
  • the magnet which may comprise weak ceramic magnetic materials, but also form pole shoes which conduct the magnetic field across the air gaps 110 and 111 between the rotor walls and the bearing 100, as indicated by broken lines and arrows by way of example.
  • the magnetic circuit containing the permanent magnet 109 passes through both walls 107 and 108, the core 105 and the air gaps defined between the core and the inner and outer walls, and pass in the same direction through both air gaps.
  • the magnetic flux produced by the winding 106 in the other magnetic flux path flows in opposite directions through the two air gaps at opposite sides of the rotor.
  • the magnetic fields in the air gaps can be strengthened and weakened in opposite directions in order to apply a net force to the rotor to the left or to the right in order to control the rotor position.
  • the embodiment of FIG. 13 can introduce advantages.
  • the bearing 100 can be made thinner, in a radial direction, than the permanent magnet lying axially inwardly thereof. Therefore, the winding 106 can be made from a shorter length of wire whereby to reduce the ohmic resistance of the bearings.
  • the annular magnet does not have to conform in shape to the bearing so that a larger volume of permanent magnetic material can be used without introducing constructive difficulties.
  • Embodiments in which the permanent magnets are mounted on rotors are not limited to the kind illustrated in FIG. 13.
  • one of the ferromagnetic wall parts 107 and 108 can be omitted. This dispenses with the doubled-up air gap, yet the mode of operation remains substantially the same.
  • first means defining a first flux path
  • a bearing according to claim 1 which is a linear bearing.
  • said first means defines two separate flux paths each with a permanent magnet therein, each of said two separate flux paths including a respective one of said two gaps.
  • a bearing according to claim 1 in which said body and said bearing define two gaps therebetween, said first and second flux paths each including portions in both of said gaps, which portions are substantially parallel to one another where they are commonly situated.
  • a bearing according to claim 10 which includes at least two permanent magnets in said first flux path, said permanent magnets being disposed side-by-side with opposite poles adjacent one another.
  • a bearing according to claim 11 in which said permanent magnets are arranged next to one another in relation to the direction of movement of said body relative to said bearing.
  • a bearing according to claim 11 which includes a plurality of permanent magnets in said first flux path, said permanent magnets being arranged side-by-side with opposite poles next to one another, and in which said electromagnet winding is divided into sections,
  • a bearing according to claim 1 which comprises a radial bearing.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Electromagnetism (AREA)
  • Magnetic Bearings And Hydrostatic Bearings (AREA)
US342892A 1972-03-20 1973-03-19 Magnetic bearings Expired - Lifetime US3890019A (en)

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DE2213470A DE2213470C3 (de) 1972-03-20 1972-03-20 Magnetisches Lager

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US3890019A true US3890019A (en) 1975-06-17

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DE (1) DE2213470C3 (de)
FR (1) FR2331254A5 (de)
GB (1) GB1424072A (de)

Cited By (54)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4012083A (en) * 1974-05-09 1977-03-15 Societe Anonyme Dite: Societe Europeenne De Propulsion Magnetic bearings
US4037886A (en) * 1974-04-30 1977-07-26 Padana Ag Bearings
US4065189A (en) * 1975-10-14 1977-12-27 Honeywell Inc. Magnetically suspended angular momentum wheel
US4180946A (en) * 1975-10-02 1980-01-01 Maurice Brunet Tool holding spindle assembly particularly for a grinding machine
US4245869A (en) * 1978-08-07 1981-01-20 Padana Ag Magnetic bearings
US4268095A (en) * 1978-12-01 1981-05-19 Massachusetts Institute Of Technology Magnetic bearing
US4305081A (en) * 1976-03-19 1981-12-08 Rca Corporation Multilayer record blank for use in optical recording
US4325586A (en) * 1979-02-28 1982-04-20 Societe Nationale Industrielle Aerospatiale Electromagnetic process for controlling orientation of a platform and platform for carrying out said process
US4337981A (en) * 1974-08-05 1982-07-06 Peter Meinke Drive and support arrangement for a disc-shaped rotor
US4387935A (en) * 1980-12-08 1983-06-14 The United States Of America As Represented By The Administrator Of The National Aeronautics And Space Administration Linear magnetic bearing
US4392168A (en) * 1978-08-16 1983-07-05 Matsushita Electric Industrial Co., Ltd. Rotary head assembly
US4398773A (en) * 1979-05-12 1983-08-16 Kernforschungsanlage Julich Gesellschaft Mit Beschrankter Haftung Magnetic suspension assembly for a rotor
US4500142A (en) * 1982-06-17 1985-02-19 Societe Europeenne De Propulsion Magnetic suspension device of a rotor placed in a sealed enclosure
US4620752A (en) * 1984-03-13 1986-11-04 Kernforschungsanlage Julich Gesellschaft Mit Beschrankter Haftung Magnetic bearing having triaxial position stabilization
US4717315A (en) * 1981-09-04 1988-01-05 Masaharu Miki Small size axial-flow molecular pump using a magnetic bearing
US4812694A (en) * 1974-09-12 1989-03-14 Kernforschungsanlage Julich Gesellschaft Mit Beschrankter Haftung Contact free magnetic bearing
US5044364A (en) * 1989-06-19 1991-09-03 Primed Products, Inc. Method and apparatus for flowing conditioned air onto person
US5068558A (en) * 1988-10-07 1991-11-26 Nippon Ferrofluidics Corporation Magnetic bearing device
US5101130A (en) * 1988-06-02 1992-03-31 Glacier Metal Company Limited Magnetic thrust bearings
US5111102A (en) * 1989-05-25 1992-05-05 Meeks Crawford R Magnetic bearing structure
WO1992010871A1 (en) * 1990-12-04 1992-06-25 University Of Houston High temperature superconducting magnetic bearings
US5126610A (en) * 1988-03-12 1992-06-30 Kernforschungsanlage Julich Gesellschaft Mit Beschrankter Haftung Axially stabilized magnetic bearing having a permanently magnetized radial bearing
US5159219A (en) * 1991-05-16 1992-10-27 University Of Houston-University Park Opposed-magnet bearing with interposed superconductor
US5216308A (en) * 1989-05-25 1993-06-01 Avcon-Advanced Controls Technology, Inc. Magnetic bearing structure providing radial, axial and moment load bearing support for a rotatable shaft
US5220222A (en) * 1991-12-23 1993-06-15 Eastman Kodak Company Magnetic bushings for an optical access actuator
US5250865A (en) * 1992-04-30 1993-10-05 Avcon - Advanced Controls Technology, Inc. Electromagnetic thrust bearing for coupling a rotatable member to a stationary member
US5270601A (en) * 1991-10-17 1993-12-14 Allied-Signal, Inc. Superconducting composite magnetic bearings
US5315197A (en) * 1992-04-30 1994-05-24 Avcon - Advance Controls Technology, Inc. Electromagnetic thrust bearing using passive and active magnets, for coupling a rotatable member to a stationary member
US5462470A (en) * 1992-10-26 1995-10-31 Seiko Seiki Kabushiki Kaisha Grinding wheel spindle assembly
US5481146A (en) * 1993-09-10 1996-01-02 Park Square, Inc. Passive null flux coil magnetic bearing system for translation or rotation
US5514924A (en) * 1992-04-30 1996-05-07 AVCON--Advanced Control Technology, Inc. Magnetic bearing providing radial and axial load support for a shaft
US5685700A (en) * 1995-06-01 1997-11-11 Advanced Bionics, Inc. Bearing and seal-free blood pump
EP0818244A1 (de) * 1996-07-10 1998-01-14 Sames S.A. Kombiniertes Magnet-Flüssigkeits-Lager für eine Turbine
US5924848A (en) * 1995-06-01 1999-07-20 Advanced Bionics, Inc. Blood pump having radial vanes with enclosed magnetic drive components
US5938412A (en) * 1995-06-01 1999-08-17 Advanced Bionics, Inc. Blood pump having rotor with internal bore for fluid flow
US6206659B1 (en) 1995-06-01 2001-03-27 Advanced Bionics, Inc. Magnetically driven rotor for blood pump
WO2001048389A2 (de) * 1999-12-27 2001-07-05 Lust Antriebstechnik Gmbh Magnetisches lagersystem
US6489700B1 (en) 2000-04-26 2002-12-03 General Atomics Homopolar machine with shaft axial thrust compensation for reduced thrust bearing wear and noise
WO2003087602A1 (de) * 2002-04-12 2003-10-23 Forschungszentrum Jülich GmbH Magnetführungseinrichtung
US6700258B2 (en) 2001-05-23 2004-03-02 Calnetix Magnetic thrust bearing with permanent bias flux
US6703735B1 (en) 2001-11-02 2004-03-09 Indigo Energy, Inc. Active magnetic thrust bearing
US20040088976A1 (en) * 2002-08-20 2004-05-13 Jens-Wolf Jaisle Turbocharger with air-cooled magnetic bearing system
US20040145265A1 (en) * 2000-04-26 2004-07-29 General Atomics Homopolar machine with shaft axial thrust compensation for reduced thrust bearing wear and noise
US6770995B1 (en) * 2001-09-22 2004-08-03 Gerald K. Foshage Passive radial magnetic bearing
US20040234391A1 (en) * 2003-05-19 2004-11-25 Izraelev Valentin M. Seal and bearing-free fluid pump incorporating a passively suspended self-positioning impeller
US20050135942A1 (en) * 2003-09-25 2005-06-23 Medforte Research Foundation Streamlined unobstructed one-pass axial-flow pump
US20050135948A1 (en) * 2003-09-25 2005-06-23 Medforte Research Foundation Axial-flow blood pump with magnetically suspended, radially and axially stabilized impeller
US20050253473A1 (en) * 2004-05-13 2005-11-17 Studer Philip A Alternative magnetic bearing
US20070164626A1 (en) * 2006-01-19 2007-07-19 Jtekt Corporation Fuel-cell compressed-air supplying device
US20070224059A1 (en) * 2006-03-23 2007-09-27 Cheng-Tien Lai Miniature pump for liquid cooling system
US20080012347A1 (en) * 2004-12-30 2008-01-17 Rozmus John J Wind generator system using attractive magnetic forces to reduce the load on the bearings
US20100127589A1 (en) * 2007-04-25 2010-05-27 Siemens Aktiengesellschaft Bearing device having a shaft which is mounted magnetically such that it can rotate about an axis with respect to a stator, and having a damping apparatus
US20130082548A1 (en) * 2011-09-30 2013-04-04 Samsung Electro-Mechanics Co., Ltd. Switched reluctance motor
US9945418B1 (en) 2016-07-31 2018-04-17 Rotor Bearings Solutions International, LLC Thrust and radial magnetic bearings using combined electromagnetic and permanent magnetic flux paths

Families Citing this family (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5521856Y2 (de) * 1973-11-09 1980-05-26
FR2294430A2 (fr) * 1974-12-10 1976-07-09 Aerospatiale Volant d'inertie pour satellite
DE2457783C2 (de) * 1974-12-06 1986-10-09 Arthur Pfeiffer Vakuumtechnik Wetzlar Gmbh, 6334 Asslar Magnetische Lagerung
DE2519651B2 (de) * 1975-05-02 1979-05-31 Teldix Gmbh, 6900 Heidelberg Magnetische Lageranordnung
JPS5725868Y2 (de) * 1975-12-02 1982-06-04
FR2377551A1 (fr) * 1977-01-13 1978-08-11 Europ Propulsion Systeme de suspension magnetique demontable
JPS5515384A (en) * 1978-07-20 1980-02-02 Kubota Ltd Operation car
JPS598010Y2 (ja) * 1980-09-09 1984-03-12 航空宇宙技術研究所長 磁気軸受
JPS5819844A (ja) * 1981-07-30 1983-02-05 Toshiba Corp 回転陽極ｘ線管用磁気軸受装置
JPS58137618A (ja) * 1982-02-10 1983-08-16 Natl Aerospace Lab 磁気軸受
JPS58186144A (ja) * 1982-04-24 1983-10-31 Toshiba Corp Ｘ線管装置
US9538963B2 (en) * 2013-03-15 2017-01-10 Aktiebolaget Skf Diagnostic scanning apparatus

Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3112962A (en) * 1962-01-17 1963-12-03 Gen Motors Corp Magnetic suspension system
US3146038A (en) * 1962-02-07 1964-08-25 Gen Motors Corp Three-axis magnetic suspension
US3462666A (en) * 1964-07-24 1969-08-19 Union Oil Co Levitated reciprocating motor
US3473852A (en) * 1967-12-18 1969-10-21 Cambridge Thermionic Corp Magnetic suspension apparatus
US3490816A (en) * 1967-12-18 1970-01-20 Cambridge Thermionic Corp Regulated suspension system
US3565495A (en) * 1969-08-05 1971-02-23 Cambridge Thermionic Corp Magnetic suspension apparatus
US3638093A (en) * 1971-04-19 1972-01-25 Rohr Corp Magnetic suspension and propulsion system
US3650581A (en) * 1969-06-30 1972-03-21 Karl Boden Wilhelm Groth & Die Bearing systems
US3749528A (en) * 1970-04-01 1973-07-31 Snecma Vacuum pumps

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3243238A (en) * 1962-07-20 1966-03-29 Lyman Joseph Magnetic suspension
DE2210995C2 (de) * 1972-03-08 1974-02-21 Teldix Gmbh, 6900 Heidelberg Magnetische Vorrichtung, insbesondere für ein Schwungrad

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3112962A (en) * 1962-01-17 1963-12-03 Gen Motors Corp Magnetic suspension system
US3146038A (en) * 1962-02-07 1964-08-25 Gen Motors Corp Three-axis magnetic suspension
US3462666A (en) * 1964-07-24 1969-08-19 Union Oil Co Levitated reciprocating motor
US3473852A (en) * 1967-12-18 1969-10-21 Cambridge Thermionic Corp Magnetic suspension apparatus
US3490816A (en) * 1967-12-18 1970-01-20 Cambridge Thermionic Corp Regulated suspension system
US3650581A (en) * 1969-06-30 1972-03-21 Karl Boden Wilhelm Groth & Die Bearing systems
US3565495A (en) * 1969-08-05 1971-02-23 Cambridge Thermionic Corp Magnetic suspension apparatus
US3749528A (en) * 1970-04-01 1973-07-31 Snecma Vacuum pumps
US3638093A (en) * 1971-04-19 1972-01-25 Rohr Corp Magnetic suspension and propulsion system

Cited By (67)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4037886A (en) * 1974-04-30 1977-07-26 Padana Ag Bearings
US4012083A (en) * 1974-05-09 1977-03-15 Societe Anonyme Dite: Societe Europeenne De Propulsion Magnetic bearings
US4337981A (en) * 1974-08-05 1982-07-06 Peter Meinke Drive and support arrangement for a disc-shaped rotor
US4812694A (en) * 1974-09-12 1989-03-14 Kernforschungsanlage Julich Gesellschaft Mit Beschrankter Haftung Contact free magnetic bearing
US4180946A (en) * 1975-10-02 1980-01-01 Maurice Brunet Tool holding spindle assembly particularly for a grinding machine
US4065189A (en) * 1975-10-14 1977-12-27 Honeywell Inc. Magnetically suspended angular momentum wheel
US4305081A (en) * 1976-03-19 1981-12-08 Rca Corporation Multilayer record blank for use in optical recording
US4245869A (en) * 1978-08-07 1981-01-20 Padana Ag Magnetic bearings
US4392168A (en) * 1978-08-16 1983-07-05 Matsushita Electric Industrial Co., Ltd. Rotary head assembly
US4268095A (en) * 1978-12-01 1981-05-19 Massachusetts Institute Of Technology Magnetic bearing
US4325586A (en) * 1979-02-28 1982-04-20 Societe Nationale Industrielle Aerospatiale Electromagnetic process for controlling orientation of a platform and platform for carrying out said process
US4398773A (en) * 1979-05-12 1983-08-16 Kernforschungsanlage Julich Gesellschaft Mit Beschrankter Haftung Magnetic suspension assembly for a rotor
US4387935A (en) * 1980-12-08 1983-06-14 The United States Of America As Represented By The Administrator Of The National Aeronautics And Space Administration Linear magnetic bearing
US4717315A (en) * 1981-09-04 1988-01-05 Masaharu Miki Small size axial-flow molecular pump using a magnetic bearing
US4500142A (en) * 1982-06-17 1985-02-19 Societe Europeenne De Propulsion Magnetic suspension device of a rotor placed in a sealed enclosure
US4620752A (en) * 1984-03-13 1986-11-04 Kernforschungsanlage Julich Gesellschaft Mit Beschrankter Haftung Magnetic bearing having triaxial position stabilization
US5126610A (en) * 1988-03-12 1992-06-30 Kernforschungsanlage Julich Gesellschaft Mit Beschrankter Haftung Axially stabilized magnetic bearing having a permanently magnetized radial bearing
US5101130A (en) * 1988-06-02 1992-03-31 Glacier Metal Company Limited Magnetic thrust bearings
US5068558A (en) * 1988-10-07 1991-11-26 Nippon Ferrofluidics Corporation Magnetic bearing device
US5216308A (en) * 1989-05-25 1993-06-01 Avcon-Advanced Controls Technology, Inc. Magnetic bearing structure providing radial, axial and moment load bearing support for a rotatable shaft
US5111102A (en) * 1989-05-25 1992-05-05 Meeks Crawford R Magnetic bearing structure
US5044364A (en) * 1989-06-19 1991-09-03 Primed Products, Inc. Method and apparatus for flowing conditioned air onto person
WO1992010871A1 (en) * 1990-12-04 1992-06-25 University Of Houston High temperature superconducting magnetic bearings
US5177387A (en) * 1990-12-04 1993-01-05 University Of Houston-University Park High temperature superconducting magnetic bearings
US5159219A (en) * 1991-05-16 1992-10-27 University Of Houston-University Park Opposed-magnet bearing with interposed superconductor
US5270601A (en) * 1991-10-17 1993-12-14 Allied-Signal, Inc. Superconducting composite magnetic bearings
US5220222A (en) * 1991-12-23 1993-06-15 Eastman Kodak Company Magnetic bushings for an optical access actuator
US5250865A (en) * 1992-04-30 1993-10-05 Avcon - Advanced Controls Technology, Inc. Electromagnetic thrust bearing for coupling a rotatable member to a stationary member
US5315197A (en) * 1992-04-30 1994-05-24 Avcon - Advance Controls Technology, Inc. Electromagnetic thrust bearing using passive and active magnets, for coupling a rotatable member to a stationary member
US5514924A (en) * 1992-04-30 1996-05-07 AVCON--Advanced Control Technology, Inc. Magnetic bearing providing radial and axial load support for a shaft
US5462470A (en) * 1992-10-26 1995-10-31 Seiko Seiki Kabushiki Kaisha Grinding wheel spindle assembly
US5481146A (en) * 1993-09-10 1996-01-02 Park Square, Inc. Passive null flux coil magnetic bearing system for translation or rotation
US5685700A (en) * 1995-06-01 1997-11-11 Advanced Bionics, Inc. Bearing and seal-free blood pump
US5924848A (en) * 1995-06-01 1999-07-20 Advanced Bionics, Inc. Blood pump having radial vanes with enclosed magnetic drive components
US5938412A (en) * 1995-06-01 1999-08-17 Advanced Bionics, Inc. Blood pump having rotor with internal bore for fluid flow
US6206659B1 (en) 1995-06-01 2001-03-27 Advanced Bionics, Inc. Magnetically driven rotor for blood pump
EP0818244A1 (de) * 1996-07-10 1998-01-14 Sames S.A. Kombiniertes Magnet-Flüssigkeits-Lager für eine Turbine
FR2751028A1 (fr) * 1996-07-10 1998-01-16 Sames Sa Turbine a suspension magnetofluidique
US5893517A (en) * 1996-07-10 1999-04-13 Sames, S.A. Magnetofluidic suspension turbine
WO2001048389A2 (de) * 1999-12-27 2001-07-05 Lust Antriebstechnik Gmbh Magnetisches lagersystem
WO2001048389A3 (de) * 1999-12-27 2001-12-27 Lust Antriebstechnik Gmbh Magnetisches lagersystem
US20030001447A1 (en) * 1999-12-27 2003-01-02 Siegfried Silber Magnetic bearing system
US6794780B2 (en) 1999-12-27 2004-09-21 Lust Antriebstechnik Gmbh Magnetic bearing system
US6489700B1 (en) 2000-04-26 2002-12-03 General Atomics Homopolar machine with shaft axial thrust compensation for reduced thrust bearing wear and noise
US6628033B1 (en) 2000-04-26 2003-09-30 General Atomics Reduction of induced magnetic forces on current collectors in homopolar machines having high magnetic fields
US6856062B2 (en) 2000-04-26 2005-02-15 General Atomics Homopolar machine with shaft axial thrust compensation for reduced thrust bearing wear and noise
US20040145265A1 (en) * 2000-04-26 2004-07-29 General Atomics Homopolar machine with shaft axial thrust compensation for reduced thrust bearing wear and noise
US6700258B2 (en) 2001-05-23 2004-03-02 Calnetix Magnetic thrust bearing with permanent bias flux
US6770995B1 (en) * 2001-09-22 2004-08-03 Gerald K. Foshage Passive radial magnetic bearing
US6703735B1 (en) 2001-11-02 2004-03-09 Indigo Energy, Inc. Active magnetic thrust bearing
WO2003087602A1 (de) * 2002-04-12 2003-10-23 Forschungszentrum Jülich GmbH Magnetführungseinrichtung
US7140848B2 (en) * 2002-08-20 2006-11-28 Borgwarner Inc. Turbocharger with air-cooled magnetic bearing system
US20040088976A1 (en) * 2002-08-20 2004-05-13 Jens-Wolf Jaisle Turbocharger with air-cooled magnetic bearing system
US7052253B2 (en) 2003-05-19 2006-05-30 Advanced Bionics, Inc. Seal and bearing-free fluid pump incorporating a passively suspended self-positioning impeller
US20040234391A1 (en) * 2003-05-19 2004-11-25 Izraelev Valentin M. Seal and bearing-free fluid pump incorporating a passively suspended self-positioning impeller
US7070398B2 (en) 2003-09-25 2006-07-04 Medforte Research Foundation Axial-flow blood pump with magnetically suspended, radially and axially stabilized impeller
US20050135948A1 (en) * 2003-09-25 2005-06-23 Medforte Research Foundation Axial-flow blood pump with magnetically suspended, radially and axially stabilized impeller
US20050135942A1 (en) * 2003-09-25 2005-06-23 Medforte Research Foundation Streamlined unobstructed one-pass axial-flow pump
US7229258B2 (en) 2003-09-25 2007-06-12 Medforte Research Foundation Streamlined unobstructed one-pass axial-flow pump
US20050253473A1 (en) * 2004-05-13 2005-11-17 Studer Philip A Alternative magnetic bearing
US20080012347A1 (en) * 2004-12-30 2008-01-17 Rozmus John J Wind generator system using attractive magnetic forces to reduce the load on the bearings
US7391128B2 (en) * 2004-12-30 2008-06-24 Rozlev Corp., Llc Wind generator system using attractive magnetic forces to reduce the load on the bearings
US20070164626A1 (en) * 2006-01-19 2007-07-19 Jtekt Corporation Fuel-cell compressed-air supplying device
US20070224059A1 (en) * 2006-03-23 2007-09-27 Cheng-Tien Lai Miniature pump for liquid cooling system
US20100127589A1 (en) * 2007-04-25 2010-05-27 Siemens Aktiengesellschaft Bearing device having a shaft which is mounted magnetically such that it can rotate about an axis with respect to a stator, and having a damping apparatus
US20130082548A1 (en) * 2011-09-30 2013-04-04 Samsung Electro-Mechanics Co., Ltd. Switched reluctance motor
US9945418B1 (en) 2016-07-31 2018-04-17 Rotor Bearings Solutions International, LLC Thrust and radial magnetic bearings using combined electromagnetic and permanent magnetic flux paths

Also Published As

Publication number Publication date
DE2213470C3 (de) 1988-12-01
JPS5858528B2 (ja) 1983-12-26
DE2213470B2 (de) 1980-04-10
JPS496334A (de) 1974-01-21
DE2213470A1 (de) 1973-10-04
GB1424072A (en) 1976-02-04
FR2331254A5 (fr) 1977-06-03

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